Axial cam gearbox mechanism

ABSTRACT

The improved gearbox mechanism of the present invention includes a plurality of cam-actuated gear block assemblies, which transfer power from a power shaft to a secondary or output gear element. Each gear block assembly includes a gear block having a surface that periodically interfaces with a secondary or output gear element. In a preferred embodiment the interface surface comprises a plurality of projections or teeth which correspond to complementary projections or gear teeth on the output gear element. Each gear block assembly further includes a gear block, a rocker arm, cam followers and/or gear block tracking post, which connect or link the gear block to a cam assembly, which in turn is connected to a power source. The cam assembly includes about its circumference a unique pathway or groove for each cam followers and/or gear block tracking post of a particular gear block assembly so that the movement of the gear block may be controlled in two or three dimensions in accordance with a certain design parameter.

CROSS-REFERENCE TO RELATED APPLICATION

This application is a continuation-in-part application of U.S. patentapplication Ser. No. 16/194,053 filed Nov. 16, 2018, which is acontinuation-in-part application of U.S. patent application Ser. No.14/995,094 filed Jan. 13, 2016 (now U.S. Pat. No. 10,260,606), which isa continuation application of U.S. patent application Ser. No.13/795,488 filed Mar. 12, 2013 (now U.S. Pat. No. 9,261,176), thetechnical disclosures of which are hereby incorporated herein byreference. This application is also related to and acontinuation-in-part application of U.S. patent application Ser. No.16/266,629 filed Feb. 4, 2019, which is a continuation-in-partapplication of U.S. patent application Ser. No. 16/111,344 filed Aug.24, 2018 (now U.S. Pat. No. 10,240,666), which is a continuation-in-partapplication of U.S. patent application Ser. No. 14/995,094 filed Jan.13, 2016 (now U.S. Pat. No. 10,260,606), which is a continuationapplication of U.S. patent application Ser. No. 13/795,488 filed Mar.12, 2013 (now U.S. Pat. No. 9,261,176), the technical disclosures ofwhich are hereby incorporated herein by reference.

BACKGROUND OF THE INVENTION Technical Field of the Invention

The present invention relates to a universal gearbox mechanism featuringcam-actuated gear block assemblies that periodically engage the outputgear causing power transfer. It has particular, but not exclusive,application for use in servomotor assemblies.

Description of the Related Art

Conventional machines typically consist of a power source and a powertransmission system, which provides controlled application of the power.A variety of proposals have previously been made in the art of powertransmission systems. The simplest transmissions, often called gearboxesto reflect their simplicity (although complex systems are also calledgearboxes in the vernacular), provide gear reduction (or, more rarely,an increase in speed), sometimes in conjunction with a change indirection of the powered shaft. A transmission system may be defined asan assembly of parts including a speed-changing gear mechanism and anoutput shaft by which power is transmitted from the power source (e.g.,electric motor) to an output shaft. Often transmission refers simply tothe gearbox that uses gears and gear trains to provide speed and torqueconversions from a power source to another device.

Gearboxes have been used for many years and they have many differentapplications. In general, conventional gearboxes comprise four mainelements: power source; drive train; housing and output means. The powersource places force and motion into the drive train. The power sourcemay be a motor connected to the drive train through suitable gearing,such as a spur, bevel, helical or worm gear.

The drive train enables the manipulation of output motion and force withrespect to the input motion and force provided by the power source. Thedrive train typically comprises a plurality of gears of varyingparameters such as different sizes, number of teeth, tooth type andusage, for example spur gears, helical gears, worm gears and/or internalor externally toothed gears.

The gearbox housing is the means which retains the internal workings ofthe gearbox in the correct manner. For example, it allows the powersource, drive train and output means to be held in the correctrelationship for the desired operation of the gearbox. The output meansis associated with the drive train and allows the force and motion fromthe drive train to be applied for an application. Usually, the outputmeans exits the gearbox housing.

The output means typically can be connected to a body whereby theresultant output motion and force from the drive train is transmittedvia the output means (e.g., an output shaft) to the body to impart theoutput mean's motion and force upon the body. Alternatively, the outputmeans can impart the motion and force output from the drive train to thegearbox housing whereby the output means is held sufficiently as toallow the gearbox housing to rotate.

Rotating power sources typically operate at higher rotational speedsthan the devices that will use that power. Consequently, gearboxes notonly transmit power but also convert speed into torque. The torque ratioof a gear train, also known as its mechanical advantage, is determinedby the gear ratio. The energy generated from any power source has to gothrough the internal components of the gearbox in the form of stressesor mechanical pressure on the gear elements. Therefore, a criticalaspect in any gearbox design comprises engineering the proper contactbetween the intermeshing gear elements. These contacts are typicallypoints or lines on the gear teeth where the force concentrates. Becausethe area of contact points or lines in conventional gear trains istypically very low and the amount of power transmitted is considerable,the resultant stress along the points or lines of contact is in allcases very high. For this reason, designers of gearbox devices typicallyconcentrate a substantial portion of their engineering efforts increating as large a line of contact as possible or create as manysimultaneous points of contacts between the two intermeshed gears inorder to reduce the resultant stress experienced by the respective teethof each gear.

Another important consideration in gearbox design is minimizing theamount of backlash between intermeshing gears. Backlash is the strikingback of connected wheels in a piece of mechanism when pressure isapplied. In the context of gears, backlash (sometimes called lash orplay) is clearance between mating components, or the amount of lostmotion due to clearance or slackness when movement is reversed andcontact is re-established. For example, in a pair of gears backlash isthe amount of clearance between mated gear teeth.

Theoretically, backlash should be zero, but in actual practice somebacklash is typically allowed to prevent jamming. It is unavoidable fornearly all reversing mechanical couplings, although its effects can benegated. Depending on the application it may or may not be desirable.Typical reasons for requiring backlash include allowing for lubrication,manufacturing errors, deflection under load and thermal expansion.Nonetheless, low backlash or even zero backlash is required in manyapplications to increase precision and to avoid shocks or vibrations.Consequently, zero backlash gear train devices are in many casesexpensive, short lived and relatively heavy.

Weight and size are yet another consideration in the design ofgearboxes. The concentration of the aforementioned stresses on points orlines of contact in the intermeshed gear trains necessitates theselection of materials that are able to resist those forces andstresses. However, those materials are oftentimes relatively heavy, hardand difficult to manufacture.

Thus, a need exists for an improved and more lightweight gearboxmechanism, which is capable of handling high stress loads in points orlines of contact between its intermeshed gears. Further, a need existsfor an improved and more lightweight gearbox mechanism having low orzero backlash that is less expensive to manufacture and more reliableand durable.

SUMMARY OF THE INVENTION

The present invention overcomes many of the disadvantages of prior artgearbox mechanisms by utilizing a plurality of cam-actuated gear blockassemblies to transfer power from a power shaft to a secondary or outputgear element. In one embodiment, each gear block assembly includes agear block having a surface that periodically interfaces with asecondary or output gear element. In a preferred embodiment theinterface surface comprises a plurality of projections or teeth whichcorrespond to complementary projections or gear teeth on the output gearelement. Each gear block assembly further includes a plurality oflinkage assemblies, which connect or link the gear block to a camassembly, which in turn is connected to a power source. The cam assemblyincludes about its circumference a unique pathway or groove for eachlinkage assembly of a particular gear block assembly so that themovement of the gear block may be controlled in two dimensions inaccordance with a certain design parameter.

The gear block assembly is designed to drive its respective gear blockthrough a two-dimensional circuit in response to rotation of the camassembly. Broadly speaking, the two-dimensional circuit includes urgingthe gear block to engage a secondary or output gear element and move orrotate a specified quantum distance prior to disengaging from the outputgear element, and returning back the specified quantum distance to againreengage the secondary or output gear element once again and repeat theprocess. The travel path or circuit of each gear block is controlled byadjusting the length and configuration of the various linkage assembliesand altering the pathways or grooves formed in the cam assembly.

When adapted to a gearbox mechanism a plurality of gear block assembliesare configured about a central axis of the cam assembly. The camassembly is rotatively coupled with a power source. As the cam assemblyrotates, the cam follower elements of the respective linkage assembliesof each gear block assembly maintain contact with a particular pathwayor groove formed in the circumferential surface of the cam assembly. Thevariance of distance from the center of rotation of the differentpathways or grooves of the cam assembly causes the respective linkageassemblies to work in concert to move their respective gear blockthrough a predetermined circuit of movement. This predetermined circuitof movement of the gear block can be precisely calibrated to meetspecific engineering requirements. For example, the torque ratio andspeed reduction may be regulated and controlled by adjusting the circuitof movement of each gear block assembly.

A another embodiment of a gearbox mechanism of the present invention mayinclude a main body, an output element, and a plurality of simplifiedgear block assemblies. Additionally, the gearbox mechanism may have aretainer that interfaces with the main body and the output element. Eachsimplified gear block assembly includes a gear block, a torque lever,cam follower(s), and/or socket (or a portion of a socket). The camactuated gear block assemblies are configured about a central axis. Therotational force on the cam element allows for a driving or rotativeforce on the cam actuated gear block assemblies.

In a preferred embodiment, the torque lever also has a set of camfollowers allowing for the following of a specified path formed along aplanar surface of the cam element. The cam element includes at least oneunique pathway or groove that interfaces with the cam follower of gearblock or torque lever so that as the cam element rotates, the movementof the gear block or torque lever is controlled in two dimensions inaccordance with at least one certain design parameter.

By varying the radius of the pathway or grooves on the cam element, thecam actuated gear block assemblies drive respective gear block(s)through a two-dimensional circuit in response to rotation of the camelement. Broadly speaking, the two-dimensional circuit includes urgingthe gear block to engage the output element and move and/or rotate theoutput element a specified distance prior to disengaging from the outputelement, and returning back the specified distance to again reengage theoutput element once again, and repeat the process. The travel path orcircuit of each gear block is controlled by adjusting the length, width,height, and/or size of the respective gear block and/or torque leverand/or altering the pathways or grooves formed in the cam element. In apreferred embodiment, there is at least one pivot point for both thegear block and the torque lever that allows each to pivot separatelyfrom each other.

Another embodiment of the gearbox mechanism of the present invention mayinclude a cam element, a main body and output element and a plurality ofsimplified gear block assemblies. In at least one example, the outputelement is retained within the main body by a retainer. The gear blockassemblies are placed within the main body and interface with the outputelement and cam element. The gear block assemblies can include a rockerarm, a gear block, a cam follower, and a pathway tracker. The camfollower and/or pathway tracker follow pathways in the cam elementand/or an axial cam to generate forces on the rocker arm and/or the gearblock(s) generating a pivoting motion for the both the rocker arm andthe gear block(s). In at least one version, the pivoting motion can be agenerally square pivot path for the gear block(s). While in otherversions, the pivot path of the gear block(s) will generally be oval orcircular.

In at least one variant embodiment, a central aperture aligned with acentral axis may be a part of the gearbox mechanism. Each gear blockassembly includes a gear block, a rocker arm, and at least one camfollower, which connect the gear block to the planar surface of the camelement. The rocker arm, and/or gear block can interact to be pivotallyattached, and correspond to the interaction and/or engagement of the camfollower(s) with the cam element. The rotation of the output element mayalso be controlled through a reverse or tension engagement (i.e.,negative bias) of gear block(s) that are not in a driving or positivebias rotational engagement in order to reduce and/or element backlash.

In at least one version, the main body provides a housing for the gearassemblies. The gear block assemblies rest and/or are supported by themain body retaining surface. The gear block(s) may also be retainedand/or supported by the main body gear block interface surface. Therocker arm(s) may also be supported and/or retained by the main bodyinterface surface, and/or the main body rocker arm void as defined bythe main body. The pivoting motion of the rocker arm can also coincidewith a pivoting motion of the gear block that allows for theinterfacing, engaging, and/or rotating of an output element.

Numerous embodiments of gearbox mechanisms are possible using the gearblock assembly of the present invention. The plurality of gear blockassemblies configured about the central axis of the cam assembly cancomprise either an odd or even number of gear block assemblies. At leasttwo, and preferably three gear block assemblies are required for agearbox mechanism of the present invention. The movement of the gearblock assemblies typically move in a rotational series to one another.At least one gear block assembly is always engaged with the output gearelement at any particular instance in time. Preferably, only one gearblock assembly is disengaged with the output gear element at anyparticular instance in time. However, in another preferred embodimentwherein the plurality of gear block assemblies comprises four or moreeven-numbered gear block assemblies, the gear block assembliesconfigured on opposing sides of the cam assembly engage and disengage inunison from the secondary or output gear element.

The design of the gear block assemblies of the present invention enablea greater number of gear teeth to engage the output gear at any giventime, thereby spreading the stresses associated therein across a greaterarea. By dramatically increasing the contact area between the gear blockand the output gear at any given time the mechanical stress level issignificantly decreased. In addition, the gear block assemblies of thepresent invention reduce backlash to zero and even preloaded conditionsto create a tight connection between the power source and the powereddevice. This is an extremely desirable feature especially for highvibration applications. By reducing backlash to zero or preloadedcondition, the mechanical impedance may also be reduced at a broad rangeof high vibration frequencies. Moreover, because the stresses associatedwith engagement of the gear block against the output gear aredistributed across a greater area, the gear block mechanism may bemanufactured of lighter weight, more flexible materials, which are lessexpensive and easier to manufacture, with no degradation in reliability.Indeed, using flexible materials further reduces the mechanicalimpedance at low frequencies. By reducing its weight and size, thegearbox mechanism of the present invention is adaptable to a broad rangeof applications that were previously impractical because of weight andspace limitations.

BRIEF DESCRIPTION OF THE DRAWINGS

A more complete understanding of the method and apparatus of the presentinvention may be had by reference to the following detailed descriptionwhen taken in conjunction with the accompanying drawings, wherein:

FIG. 1A is a perspective view of a first embodiment of a gearboxmechanism attached to a power source as previously disclosed inco-pending application Ser. No. 16/194,053, the disclosure of which isfully incorporated herein by reference;

FIG. 1B is a side elevation view thereof;

FIG. 2 is an end view thereof with the outer stationary plate removed;

FIG. 3 is a perspective view of a second embodiment of a gearboxmechanism as previously disclosed in co-pending application Ser. No.16/266,629, the disclosure of which is fully incorporated herein byreference;

FIG. 4 is an illustration of an exploded perspective view of a thirdembodiment of a gearbox mechanism of the present invention;

FIG. 5 is an illustration of a perspective view of an output element,cam element, and gear block assembly thereof;

FIG. 6 is an illustration of an alternative perspective view of a hub,gear block assemblies, and output element thereof;

FIG. 7 is an illustration of a side view a hub, gear block assemblies,and output element thereof;

FIG. 8 is a perspective view illustration of a main body of the gearboxmechanism shown in FIG. 4;

FIG. 9 is a perspective view illustration of an axial cam of the gearboxmechanism shown in FIG. 4;

FIG. 10 is an alternative perspective view of the axial cam thereof;

FIG. 11 is an illustration in perspective view of an output element ofthe gearbox mechanism shown in FIG. 4;

FIG. 12 is a perspective view illustration of a cam element of thegearbox mechanism shown in FIG. 4;

FIG. 13 is a front perspective view of a gear block of the gearboxmechanism shown in FIG. 4.

FIG. 14 is a rear perspective view of the gear block thereof;

FIG. 15 is a top perspective view of a rocker arm of the gearboxmechanism shown in FIG. 4;

FIG. 16 is a bottom perspective view of the rocker arm thereof;

FIG. 17 is an illustration of an exploded perspective view of a fourthembodiment of a gearbox mechanism of the present invention;

FIG. 18 is a perspective view illustration of a cam element and gearblock assembly of the gearbox mechanism shown in FIG. 17;

FIG. 19 is an illustration of a perspective view of the cam elementtherof;

FIG. 20 is an illustration of an alternative perspective view of the camelement thereof;

FIG. 21 is a sectional view illustration of the cam element and gearblock assembly of the gearbox mechanism shown in FIG. 17;

FIG. 22 is another sectional view illustration of the cam element andgear block assembly of the gearbox mechanism shown in FIG. 17;

FIG. 23 is a perspective view illustration of a gear block assembly ofthe gearbox mechanism shown in FIG. 17;

FIG. 24 is a front perspective view of a gear block of the gear blockassembly shown in FIG. 23;

FIG. 25 is a rear perspective view of the gear block thereof;

FIG. 26 is a front side view of a rocker arm of the gear block assemblyshown in FIG. 23;

FIG. 27 is a rear side view of the rocker arm thereof;

FIG. 28 is a perspective view of a rocker block of the gear blockassembly shown in FIG. 23;

FIG. 29 is a perspective view of a rocker pin of the gear block assemblyshown in FIG. 23; and

FIG. 30 is a perspective view of a main body of the gearbox mechanismshown in FIG. 17.

Where used in the various figures of the drawing, the same numeralsdesignate the same or similar parts. Furthermore, when the terms “top,”“bottom,” “first,” “second,” “upper,” “lower,” “height,” “width,”“length,” “end,” “side,” “horizontal,” “vertical,” and similar terms areused herein, it should be understood that these terms have referenceonly to the structure shown in the drawing and are utilized only tofacilitate describing the invention.

All figures are drawn for ease of explanation of the basic teachings ofthe present invention only; the extensions of the figures with respectto number, position, relationship, and dimensions of the parts to formthe preferred embodiment will be explained or will be within the skillof the art after the following teachings of the present invention havebeen read and understood. Further, the exact dimensions and dimensionalproportions to conform to specific force, weight, strength, and similarrequirements will likewise be within the skill of the art after thefollowing teachings of the present invention have been read andunderstood.

DETAILED DESCRIPTION OF THE INVENTION

With reference to the Figures, and in particular FIGS. 1A, 1B and 2, anembodiment of a machine 10 utilizing a gearbox mechanism 20 is depictedas previously disclosed in co-pending application Ser. No. 16/194,053,the disclosure of which is fully incorporated herein by reference. Themachine 10 includes a power source or actuator 2, which includes anoutput device (not illustrated) that transmits the power generated bythe power source 2. While the embodiment shown in the Figure generallydepicts the power source 2 as an electric motor and the output device asan output shaft of the electric motor, it is understood that there arenumerous possible embodiments. For example, output device need not bedirectly connected to the power source 2 but may be rotatively coupledby means of gears, chains, belts or magnetic fields. Likewise, the powersource 2 may comprise an electric motor, an internal combustion engine,or any conventional power source that can be adapted to generaterotative power in an output device. Moreover, the power source 2 mayalso comprise the output gear of a preceding gear train mechanism.

As shown in the embodiment depicted in FIGS. 1A, 1B and 2, the pluralityof cam-actuated gear block assemblies 60 transfer power from the powershaft 4 to an annular secondary or output gear element 50. In apreferred embodiment, each gear block assembly 60 includes a gear block62 having an interface surface 63 (e.g., a plurality of projections orteeth 66) which correspond to a complementary interface surface 54(e.g., projections or gear teeth) configured on an inner circumferentialsurface 53 of the annular secondary or output gear element 50. It isunderstood that the interface between the gear block 62 and the innercircumferential surface 53 of the output gear element 50 of the presentinvention comprises not only the preferred gear teeth as depicted, butalso any complementary arrangement such as pins and holes or evenfriction fit surfaces.

While the annular output or power gear element 50 is depicted as twocircular rings held apart by spacer elements 55, it is understood thatthe output or power gear element 50 may comprise a single circular ring.The output or power gear element 50 includes apertures or holes 58 forattaching to an output shaft or power takeoff (not shown). In addition,it is understood that the outer circumference 51 of the output or powergear element 50 may also comprise a surface to interface with some othergear train mechanism.

The gear blocks 62 of the present invention are specifically designed toenable a greater surface area (e.g., greater number of gear teeth) toengage the output gear 50 at any given time, thereby spreading thestresses associated therein across a greater area. By dramaticallyincreasing the contact area between the gear block 62 and the outputgear 50 at any given time the mechanical stress level is significantlydecreased. In addition, the gear block 62 assemblies of the presentinvention reduce backlash to zero and even preloaded conditions tocreate a tight connection between the power source 2 and the powereddevice. This is an extremely desirable feature especially for highvibration applications. Moreover, because the stresses associated withengagement of the gear block 62 against the output gear 50 aredistributed across a greater area, the gear block 62 may be manufacturedof lighter weight materials, which are typically less expensive andeasier to manufacture, with no degradation in reliability. For example,per Hertz Contact Theory a typical stress result for spur gears are inthe range from 450 MPa to 600 MPa. High grade steels are the best fittedmaterials for handling such high stress levels. Other materials like lowgrade steel or aluminum will deform under the similar conditions.However, by distributing the stresses across a large area of contact inaccordance with the gearbox mechanism of the present invention, thelevels of stress under the similar conditions can be reduced to about 20MPa. These low stress levels allow the gearbox mechanism of the presentinvention to be manufactured using low grade steels, aluminums or evenplastics for the same application. By reducing its weight and size, thegearbox mechanism of the present invention is adaptable to a broad rangeof applications that were previously impractical because of weight andspace limitations.

The cam assembly 30 is coupled to the power source 2 by means of theoutput device or power shaft (not illustrated). Thus, power generated bythe power source 2 is transferred to the power shaft, which causes thecam assembly 30 to rotate about the central axis 6. The cam assembly 30includes about its circumferential surface 34 a plurality of uniquepathways or grooves which each interface with the cam follower elementof a single linkage assembly of each gear block assembly 60 so that asthe cam assembly 30 rotates, the movement of the gear block 62 iscontrolled in two dimensions in accordance with a certain designparameter. By varying the radius of the pathway or grooves on the camassembly 30 the linkage assemblies of the gear block assembly 60 driverespective gear block 62 through a two-dimensional circuit in responseto rotation of the cam assembly 30. Broadly speaking, thetwo-dimensional circuit includes urging the gear block to engage theoutput gear element 50 and move or rotate the output gear element 50 aspecified quantum distance prior to disengaging from the output gearelement 50, and returning back the specified quantum distance to againreengage the output gear element 50 once again and repeat the process.The travel path or circuit of each gear block 62 is controlled byadjusting the length and configuration of the various linkage assembliesand altering the pathways or grooves formed in the cam assembly 30.

In a preferred embodiment, each linkage mechanism includes two pivotallycoupled connector arms. An upper connector arm includes a first pivotpoint that is pivotally coupled to its respective gear block 62 and asecond pivot point pivotally coupled to a lower connector arm. The lowerconnector arm includes a cam follower element at its distal end thatmaintains contact with its respective pathway or groove formed in thecam assembly 30. The lower connector arm further includes a pivot pointhaving a fixed axis of rotation relative to the central axis 6 ofrotation of the cam assembly 30.

With reference now to FIG. 3 an illustration of a second embodiment of agearbox mechanism is depicted as previously disclosed in co-pendingapplication Ser. No. 16/266,629, the disclosure of which is fullyincorporated herein by reference. FIG. 3 depicts a perspective view ofthe gear block assemblies 260 interfacing with an output element 250 ofthe gearbox mechanism. The gear block assemblies 260 can include a gearblock 262, a torque lever 299, a first cam follower 294A, and/or asecond cam follower 294B. In at least one version the first cam follower294A is coupled to the gear block 262, and the second cam follower 294Bis coupled to the torque lever 299. As the cam followers 294A/294Btraverse the first and second pathways 236/237 they generate radial andangular movements of the torque lever 299 and/or the gear block 262.These longitudinal and latitudinal movements of the torque lever 299and/or gear block 262 allow for and/or generate the pivot movements ofthe torque lever 299, and/or gear block 262. In at least one example, aspacer 246 can be utilized to support and/or engage the torque lever299.

The torque lever pivot post 288 and the gear block pivot void 297interact to generate forces that cause the gear block 262 to engageand/or disengage from the output element 250. The movement of a gearblock 262, in at least one example, is a cyclical, annular or closedloop movement that may have a generally rectangular, elliptical,circular, square, conical, oval, ovoid, truncated circular pattern, orany combination thereof, design specified pattern of movement.

For example, a gear block interface surface 263 can engage and/ordisengage from an output element interface surface. The gear block 262will move in a cyclical manner as a result of the pivot movements of thetorque lever 299 and cam followers 294A/294B. In at least one version,the gear block can have four positions. A first position 228 (ortransitioning position) allows for the gear block to traverse or move toa new position to begin a new rotation of the output element 250. Thesecond position 226 (or engaged or positive bias movement position)allows for the gear block to generate a rotational or pulling force 228on the output element 250. The third position 225 (or neutral orbalanced position) may allow the gear block 262 to be in a position toengage, rotate, or disengage from the output element interface surfacewith no forces generated on the output element. The fourth position 227(i.e., reverse tension or negative bias configuration) allows for atension to be placed on the output element 250 to assist in theprevention and/or elimination of backlash of the output element 250.

The cam element guide 216 can be interfaced with the output element 250through a rotational support, ball bearing assembly, and/or set of ballbearings (not illustrated) that can be placed between the cam elementguide circumferential surface 217 and the output element circumferentialsurface 251.

As shown in the embodiment depicted in the Figures, the plurality ofcam-actuated gear block assemblies 260 transfer power from an input orrotating device (not illustrated) to an output element 250. In apreferred embodiment, each gear block assembly 260 includes a gear block262 having an interface surface 263 (e.g., a plurality of projections orteeth 266) which correspond to a complementary output element interfacesurface 254 (e.g., projections or gear teeth) configured on an outercircumferential surface 251 of the output element 250. The presentinvention comprises not only the preferred gear teeth as depicted, butalso any complementary arrangement such as pins and holes or evenfriction fit surfaces.

While the output element 250 is depicted as a single circular ring, itis understood that the output element 250 may comprise two circularrings held apart by spacer elements (not illustrated). The outputelement 250 includes apertures or holes 258 for attaching to an outputshaft or power takeoff (not illustrated). In addition, it is understoodthat the inner circumference 251 of the output element 250 may alsocomprise a surface to interface with some other gear train mechanism.

In addition, it is understood that the gear block 262 may include adivider/alignment block (not illustrated) dividing the interface surface263 into two separate sections. The variant of the gear block 262featuring the alignment block (not illustrated) is particularly suitableto embodiments which feature output elements 250 comprised of circularrings. The gear block 262 can have a gear block post 264 that mayinteract with a torque lever aperture 297 to provide a pivot point forthe gear block 262 and/or torque lever 299.

The gear blocks 262 of the present invention are specifically designedto enable a greater surface area (e.g., greater number of gear teeth) toengage the output element 250 at any given time, thereby spreading thestresses associated therein across a greater area. By dramaticallyincreasing the contact area between the gear block 262 and the outputelement 250 at any given time the mechanical stress level issignificantly decreased. In addition, the gear block 262 assemblies 260of the present invention reduce backlash to zero and even preloadedconditions to create a tight connection between the power source and/orthe powered device (not illustrated). This is an extremely desirablefeature especially for high vibration applications. Moreover, becausethe stresses associated with engagement of the gear block 262 againstthe output element 250 are distributed across a greater area, the gearblock 262 may be manufactured of lighter-weight materials, which aretypically less expensive and easier to manufacture, with no degradationin reliability.

The cam element 230 can be coupled to an input device, power source, orother rotating device (not illustrated) by means of a shaft, gears,belts, magnetic fields, friction fit, or other means of coupling. Powergenerated by an input device, power source, or other rotating device(not illustrated) can be transferred to a shaft, gears, belts, magneticfields, friction fit, or other means of coupling, which causes the camelement 230 to rotate about the central axis 206. The cam assembly 230includes along its planar surface a plurality of unique pathways orgrooves which each interface with the cam follower(s) 294 of a gearblock assembly 260 so that as the cam element 230 rotates, the movementof the gear block 262 is controlled in two dimensions in accordance witha certain design parameter. By varying the radius of the pathway orgrooves on the cam element 230 the gear block assemblies 260 driverespective gear block(s) 262 through a two-dimensional circuit inresponse to rotation of the cam element 230. Broadly speaking, thetwo-dimensional circuit includes urging the gear block 262 to engage theoutput element 250 and move or rotate the output element 250 a specifieddistance prior to disengaging from the output element 250, and returningback the specified distance to again reengage the output element 250once again and repeat the process. The travel path or circuit of eachgear block 262 is controlled by adjusting the size, height, length andconfiguration of the torque lever(s) 299, gear block(s) 262, and/or camfollower(s) 294 and altering the pathways or grooves formed in the camelement 230.

For example, the pivotal connections may further include torsionalspring elements (not shown) which bias the torque lever 299, and/or gearblock 262 so that the cam follower 294 maintains contact with thesurface of its respective pathway or groove 236, 237 formed in theplanar surface 235 of the cam element 230 throughout the rotation cycleof the cam element 230. In one embodiment, the planar surface of the camassembly 230 is substantially perpendicular to the axis of rotation ofthe cam assembly 230. Alternatively, or in addition, a ring springconnecting all of the gear blocks 262 in a gear train may be used as abiasing mechanism in accordance with the present invention.

The gear block assemblies 260 are biased and/or secured so that each camfollower 294 maintains contact with the surface of its respectivepathway or groove formed in the cam element 230 throughout the rotationcycle of the cam element 230. For example, cam follower 294A maintainscontact with the surface of a first pathway 236, and cam follow 294Bmaintains contact with the surface of a second pathway 237. Each pathwayhas a unique circumference, the radius of which varies over the courseof the pathway.

By varying the radius of each pathway or groove 236, 237 on the camelement 230, torque lever(s) 299 drive their respective gear block(s)262 through a two-dimensional circuit in response to rotation of the camelement 230. In general, the two-dimensional circuit 239 includes urgingthe gear block 262 to engage the output element 250 and move or rotatethe output element 250 a specified distance prior to disengaging formthe output element 250, and returning back the same specified distanceto again reengage the output element 250 once again and repeat theprocess. It is understood that the two-dimensional circuit 239 depictedin the drawings is not to scale and is somewhat exaggerated toillustrate the general principal of the invention. For example, thedistance A-B would typically be much smaller than depicted. The travelpath or circuit 239 of each gear block 262 is controlled by adjustingthe size and configuration of the torque lever(s) 299, gear block(s)262, and/or altering the pathways or grooves 236, 237 formed in the camelement 230.

When adapted to a gearbox mechanism 220, a plurality of gear blockassemblies 260 are configured about the central axis 206 of the camelement 230. The cam element 230, in at least one version, may becoupled to a power source (not illustrated) by an output device (notillustrated). As the cam element 230 rotates, the cam follower(s) 294 ofthe respective torque lever(s) 299 and/or gear block(s) 262 of each gearblock assembly 260 maintain contact with a particular pathway or groove236, 237 formed in the planar surface 235 of the cam element 230. Thevariance of distance from the center of rotation of the differentpathways or grooves 236, 237 of the cam element 230 causes the torquelever(s) 299 pivotally attached to a cam follower(s) 194 to work inconcert to move their respective gear block(s) 262 through apredetermined circuit of movement 239. This predetermined circuit ofmovement 239 of the gear block 260 can be precisely calibrated to meetspecific engineering requirements. For example, the torque ratio andspeed reduction may be regulated and controlled by adjusting the circuitof movement 239 of each gear block assembly 260.

With reference to the Figures, and in particular FIGS. 4, 5, and 6, athird embodiment of a gearbox mechanism 320 of the present invention isdepicted. The gearbox mechanism 320 may be powered and/or rotated by apower source or actuator (as shown in FIGS. 1A and 1B), that istransmitted to an output device (not illustrated) by the gearboxmechanism 320. The power source can be an electric motor, combustionengine, water activated source, wind turbine, or other possibleembodiments. Additionally, the power source or actuator, as well as theoutput device (not illustrated) may be rotatively coupled by means ofgears, chains, belts, or magnetic fields.

The gearbox mechanism 320 can be configured about a central axis 306.The central axis 306 can pass through a central aperture of the mainbody 340, the output element 350, cam element 330, axial cam 331, andhub 314. The main body 340 and the hub 314 may be coupled togetherthrough fasteners 347. The fasteners 347 may be screws, bolts, allthread, compression fit devices, or other means for fastening twocomponents together in a fixed or secure manner. There can be bearings,or roller bearings 307 that may separate each of the output element 350,axial cam 331, and cam element 330 from the main body 340 and/or the hub314. In at least one example, there may also be bearings or rollerbearings 307 that separate the output element and the axial cam 331.

In some embodiments, a cam assembly is created by coupling together theaxial cam 331 and cam element 330 using fasteners like fasteners 302,wherein the axial cam 331 and cam element 330 interact with gear blockassemblies. The fasteners 302 may be screws, bolts, all thread,compression fit devices, or other means for fastening axial cam 331 andcam element 330 together in a fixed or secure manner. The gearboxmechanism 320 further includes a plurality of gear block assemblies 360.Each gear block assembly 360 can include a rocker arm 399 (rocker arms399A, 399B, 399C, 399D, 399E, 399F, and 399G collectively referred to asrocker arm(s) 399) that are coupled with the gear block(s) 362 (gearblocks 362A, 362B, 362C, 362D, 362E, 362F, and 362G may be referred tocollectively as gear block(s) 362). The gear blocks 362 of the presentinvention are specifically designed to enable a greater surface area(e.g., greater number of gear teeth) to engage the output element 350 atany given time, thereby spreading the stresses associated therein acrossa greater area. By dramatically increasing the contact area between thegear block 362 and the output element 350 at any given time themechanical stress level is significantly decreased. In some embodimentsthe gear block(s) 362 may have a pathway tracker that can, individuallyor in combination with a pathway follower element, track and/or follow apathway formed into the axial cam 331. The pathway follower element caninclude a ball bearing, roller bearing, or other mechanism or means forreducing friction. In addition, the gear block assemblies 360 of thepresent invention reduce backlash to zero and even preloaded conditionsto create a tight connection between the power source and/or the powereddevice (not illustrated). This is an extremely desirable featureespecially for high vibration applications. Moreover, because thestresses associated with engagement of the gear block 362 against theoutput element 350 are distributed across a greater area, the gear block362 may be manufactured of lighter-weight materials, which are typicallyless expensive and easier to manufacture, with no degradation inreliability.

For example, per Hertz Contact Theory, a typical stress result for spurgears, are in the range from 450 MPa to 600 MPa. High grade steels arethe best fitted materials for handling such high stress levels. Othermaterials, like low grade steel or aluminum, will deform under thesimilar conditions. However, by distributing the stresses across largeareas of contact in accordance with the gearbox mechanism of the presentinvention, the levels of stress under the similar conditions can bereduced to about 20 MPa. These low stress levels allow the gearboxmechanism of the present invention to be manufactured using low gradesteels, aluminums or even plastics for the same application. By reducingits weight and size, the gearbox mechanism 320 of the present inventionis adaptable to a broad range of applications that were previouslyimpractical because of weight and space limitations.

In some embodiments, the rocker arm 399 can also have a cam follower 394allowing for the following of a specified pathway(s) formed in or alonga planar surface 334 of the cam element 330. While the planar surface334 in FIGS. 4, 5, and 6, is depicted on the side of the cam element 330facing the axial cam 331, it should be understood that the planarsurface, into which pathway(s) 336 may be formed, may either face theaxial cam 331 or face away from the axial cam 331. The gearbox mechanism320 can also include a hub 314 and/or a ball bearing assembly 307 thatallows the cam element 330 to rotate freely based upon an input devicesuch as a shaft or rotatable elements such as a set of other gearing,belts, levers, magnetic or electrical fields, etc. In at least oneexample, there may be multiple ball bearing assemblies 307A, 307B, 307C,307D, 307E, and/or 307F (collectively 307) that allow for reducedfriction and freedom of movement for any rotational components. Theinterface surface 363 of each gear block 362 can engage with the outputelement interface surface 353 of the output element 350. In someembodiments, the gear blocks 362 are articulated by an associatedmovement of the rocker arm 399.

The cam element 330 includes at least one unique pathway or groove 336that interfaces with the cam follower 394 of each rocker arm 399 so thatas the cam element 330 rotates, the movement of the gear block 362and/or rocker arm 399 is controlled in two dimensions in accordance withat least one certain design parameter. By varying the radius of thepathway or grooves 336 on the cam element 330, the gear block assemblies360 drive their respective gear block(s) 362 through a two-dimensionalcircuit in response to rotation of the cam element 330. Broadlyspeaking, the two-dimensional circuit includes urging the gear block(s)362 to engage the interface surface 353 of the output element 350 andmove and/or rotate the output element 350 a specified distance prior todisengaging from the output element 350, and returning back thespecified distance to again reengage the output element 350 once again,and repeat the process. The travel path or circuit of each gear block362 is controlled by adjusting the length, width, height, and/or size ofthe respective gear block and/or rocker arm and/or by altering thepathways or grooves 336 formed in the cam element 330.

The rocker arm 399 is pivoted around a specific pivot point by the camfollower 394, which traverses the pathway 336 formed in the cam element330. Additionally, the gear blocks 362 may also have a pathway trackerand/or pathway cam follower that follows a separate path along the axialcam 331 that also triggers an actuation point for the gear block(s) 362.In at least one embodiment, there is at least one pivot or actuationpoint for both the gear block(s) 362 and the rocker arm 399 that allowseach to actuate or pivot separately from each other and while alsomoving in conjunction to create a specific pattern of movement for thegear block(s) 362. The movement of a gear block 362, in at least oneexample, is a cyclical, annular or closed loop movement that may have agenerally rectangular, elliptical, circular, square, conical, oval,ovoid, truncated circular pattern, or any combination thereof, designspecified pattern of movement.

With reference now to FIG. 5, a perspective view is depicted of the camelement 330, output element 350, along with the rocker arm 399, camfollower 394, and gear block 362. The axial cam 331 is also depicted;however, in this view, it is not easily seen. A central axis 306 canpass through the central aperture 332 at the center of the cam element330, axial cam 331, and/or output element 350. In at least oneembodiment of the present disclosure, the cam element 330 interacts withthe rocker arm 399 along with the gear block 362 to rotate and cause amovement of the gear block 362 to have a cyclical, annular or closedloop movement having a generally rectangular, elliptical, circular,square, conical, oval, ovoid, truncated circular pattern, or anycombination thereof, design specified pattern of movement based upon thepathways in the cam element 330 that may allow a cam follower 394attached to the rocker arm 399 to traverse along the pathway 336 andgenerate movement of the gear block(s) 362.

Each of the cam followers 394 can each have a separate path or, in someembodiments, may have a single path that each follow at a differentposition simultaneously. The gear block(s) 362 can be pivotallyconnected to the rocker arm 399. Alternatively or in addition, a ringspring connecting all of the gear blocks 362 in a gear train may be usedas a biasing mechanism in accordance with the present invention. In atleast one embodiment of the present disclosure, the cam element willhave a single pathway, however there may be multiple pathways formed inthe cam element 330 that can be in the same plane where they areparallel paths, or pathways of different distances from the central axis306, or the pathways can be in separate planes stacked in the directionof the central axis 306.

In at least one embodiment, the pathway 336 formed in cam element 330allows for movement and rotation of the gear blocks 362 causing theinterface surfaces of the gear blocks 362 to engage, interface and/orinteract with the output element 350. Cam follower(s) 394 maintaincontact with the surface of their respective pathways or grooves formedin the cam element 330. While the cam element 330 depicted in theFigures, appears to be a single disc or unit having at least one pathwayor groove 336 formed in the planar surface 334 of the cam element 330,it is understood that the cam element 330 may also comprise a pluralityof separate discs, each having a unique pathway formed in its planarsurface (e.g., 334), which are mechanically coupled to one another toassemble a single cam assembly 330. In a preferred embodiment, theplanar surface 334 of the cam assembly 330 is substantiallyperpendicular to the axis of rotation of the cam assembly 330. While theplanar surface 334 depicted in FIG. 5 is shown as being on the side ofthe cam element 330 facing the axial cam 331, it should be understoodthat the planar surface, into which pathway(s) 336 is formed, may eitherface the axial cam 331 or face away from the axial cam 331.

For example, by varying the radius of the pathway or groove 336 on thecam element 330, the rocker arm 399 pivots about its pivot point tocompensate and maintain contact between rocker arm 399 and the main body(not illustrated). This pivoting or moving of the rocker arm 399 aboutits pivot point induces movement in the pivotal connection with the gearblock 362. Each rocker arm 399 acts independently of the other rockerarm(s) 399 due to the cam follower(s) 394 of each rocker arm 399following and/or traversing the pathway 336 formed in the planar surface334 of the cam element 330 at their respective distinct points.

As the cam followers 394 for the rocker arms 399 follow their respectivepathway(s) 336, the rocker arm 399 can pivot at a specific point causingthe gear block to pivot and/or rotate around a specific point. Forexample, the pivot point of the rocker arm 399 will trigger a left,right, in or out, or a rotational motion to the gear block 362. Ingeneral, the three-dimensional circuit may have a first portion 339Aincludes urging the gear block 362 to biasing the output element 350 andmove or rotate the output element 350 a specified distance prior toreleasing the biasing of the output element 350. Additionally, there maybe an engagement and/or disengagement actuation that results in a secondportion 339B of the three-dimensional circuit (i.e., collectively thefirst portion 339A and the second portion 339B create thethree-dimensional circuit which will be referred to as 339). Associatedtogether they allow for a cyclical, annular or closed-loop movement orcircuit 339 of the gear block and the interfacing surface that has agenerally rectangular, elliptical, circular, square, conical, oval,ovoid, truncated circular pattern, or any combination thereof, designspecified pattern of movement. The cyclical, annular or closed-loopmovement or circuit 339 of the gear block 362 can allow for a positivebiasing of the output interface surface by the gear block interfacesurface that is translated into a forward rotation of the output element350. Additionally, the gear block 362 can negatively bias the outputelement interface surface with the gear block interface surface in amanner that reduces the backlash or possible backlash of the outputelement and/or gear block. In at least one embodiment, there can also bea neutral biasing or position that allows the gear block 362 to not biasthe output element 350 in a positive and/or negative manner, it may alsoin some example allow for the gear block 362 to release outwardly fromthe central axis.

With reference now to FIGS. 5, 6, 7, 8, 9, 10, 11, and 12, additionalillustrations of the third embodiment of a gearbox mechanism 320 of thepresent invention are depicted. By varying the radius of the pathway orgroove 336 on the cam element 330, rocker arm(s) 399 drive theirrespective gear block(s) 362 through a two-dimensional circuit inresponse to rotation of the cam element 330. In general, thetwo-dimensional circuit 339A includes urging the gear block 362 tobiasing the output element 350 and move or rotate the output element 350a specified distance prior to releasing the biasing of the outputelement 350. Additionally, there may be an engagement and/ordisengagement actuation that allows for the addition of a second portion339B to the two-dimensional circuit. When the gear block is disengagedfrom the output element 350, the gear block 362 can be rotated andpivoted in a manner to allow it to move the interface surface in adirection opposite of the rotational movement of the output element 350,allowing the gear block 362 to return back the same specified distanceto again reengage the output element 350 once again and repeat theprocess. It is understood that the two-dimensional circuit 339 depictedin the drawings is not to scale and is exaggerated to illustrate thegeneral principal of the invention. For example, the distance A-B wouldtypically be much smaller than depicted. The travel path or circuit 339Aof each gear block 362 is controlled by adjusting the size andconfiguration of the rocker arm(s) 399, gear block(s) 362, and/oraltering the pathway or groove 336 formed in the cam element 330.

When adapted to a gearbox mechanism 320, a plurality of gear blockassemblies 360 are configured about the central axis 306 that passesthrough the cam element 330. The cam element 330, in at least oneversion, may be coupled to a power source (not illustrated) by an outputdevice (not illustrated). As the cam element 330 rotates, the camfollower(s) 394 of the respective rocker arms(s) 399 of each gear blockassembly maintain contact with a particular pathway or groove 336 formedin the planar surface 334 of the cam element 330. In a preferredembodiment, the planar surface 334 of the cam assembly 330 issubstantially perpendicular to the axis of rotation of the cam assembly330. The variance of distance from the center of rotation to thedifferent points along the pathway or groove 336 of the cam element 330causes the rocker arm(s) 399, pivotally attached to a gear block(s) 362to work in concert to move their respective gear block(s) 362 through apredetermined circuit of movement 339. This predetermined circuit ofmovement 339 of the gear block 362 can be precisely calibrated to meetspecific engineering requirements. For example, the torque ratio andspeed reduction may be regulated and controlled by adjusting the circuitof movement 339 of each gear block 362. An axial cam 331 rotates, incoordination with the cam element 330, and as they are rotated thepathway tracker 364 (see in particular FIGS. 7, 13 and 14) of the gearblock 362 tracks along the axial pathway or groove 337. The axialpathway or groove 337 is formed in the circumferential surface 335 ofthe axial cam 331. The variance of height of the pathway towards or awayfrom the lower section 333A of the axial cam 331, causes the gear block362 to be engaged or disengaged from the interface surface 353 of theoutput element 350 with a linear movement (may also be called a secondportion 339B of the three-dimensional circuit for the gear block 362).The movement of the gear block 362 may be created through two separateportions (339A/339B) that act in concert to generate a rotational (twodimensional movement in one plane (horizontal) a combination ofleft-right/in-out axial motions) movement and a linear movement in avertical plane (up and down motions) that create the three dimensionalcircuit.

Numerous embodiments of gearbox mechanisms are possible using the gearblock assembly of the present invention. All embodiments of gearboxmechanisms constructed in accordance with the present invention featurea plurality of gear block assemblies configured about the central axis306 of the cam element 330 and may comprise either an odd or even numberof gear block assemblies. At least two, and preferably three or more,gear block assemblies are required for a gearbox mechanism of thepresent invention. The movement of the gear block assemblies typicallymoves in a rotational series to one another.

However, in a preferred embodiment of the present invention wherein theplurality of gear block assemblies comprises four or more even-numbergear block assemblies, the gear block assemblies configured on opposingsides of the cam element 330 engage and disengage in unison from thesecondary or output element 350. For example, an embodiment of thegearbox mechanism 320 may feature four gear block assemblies 360.Similarly, another embodiment of the gearbox mechanism 320 may featuresix gear block assemblies 360. This is accomplished by ensuring that theindividual pathways or grooves formed in the planar surface of the camelement are in phase with one another along the planar surface of thecam element 330.

With reference now to FIG. 8, a perspective view of a main body 340 isshown. The main body 340, in at least one version, can provide a housingfor the gear block assemblies (not illustrated). The gear blockassemblies (not illustrated) can rest and/or be supported by the mainbody retaining surface 387. The rocker arm(s) (not illustrated) may besupported and/or retained by the main body rocker arm void 377 asdefined by the main body 340. A rocker arm post 388 (see e.g., FIG. 15)can be configured to be retained and/or supported by the main bodyrocker arm void 377 to allow for a pivoting motion of the rocker arm(see e.g., FIG. 15) to occur. For example, the main body rocker arm void377 may be sized to retain and prevent the rocker arm(s) (notillustrated) from being removed except in a single direction that isperpendicular to the pivoting motion that the rocker arm(s), while thepivoting motion of the rocker arm(s) (not illustrated) can also coincidewith a pivoting motion of the gear block (not illustrated) that allowsfor the interfacing, engaging, and/or rotating of an output element (notillustrated).

A cam interface surface 389 can support a cam element (not illustrated)as it engages with the gear assemblies (not illustrated). The main body340 can be coupled on the cam side 341 to an input hub, a retainer, orother securing devices via a fastener (not illustrated) sized to fitinto a coupling aperture 344 defined by the main body 340. The inputhub, retainer, or other securing devices, in at least one example, canbe utilized to secure and/or support a cam element (not illustrated) ina manner to prevent vibration but allow free movement of the camelement.

With reference now to FIGS. 4, 9 and 10, assorted view of the axial cam331 are depicted. The axial cam 331 can be coupled to a cam element 330through an axial cam securing aperture 345. In at least one example, theaxial cam securing aperture 345 can be a threaded aperture that allowsfor a fastener 302 to be utilized in securing the axial cam 331 and thecam element 330 in a secure and/or fixed manner. The axial cam 331 maycomprise a lower section 333A and an upper section 333B. The lowersection 333A can be a tubular section having a smooth surface forinterfacing with the output element (not illustrated) and/or bearings,roller bearing, or ball bearings. The upper section 333B can comprise aflange section have one or more axial cam securing aperture(s) 345traversing the portion of the upper section 333B that extends outwardlypast the perimeter of the lower section 333A. The circumferentialsurface 335 of the upper section 333B may have a pathway 337 formed intoit and defined by the upper section 333B of the axial cam 331. Asdepicted in FIG. 9, the axial cam pathway 337 is generally circular orannular, in a horizontal plane, while in other embodiments it will beshaped and/or configured to match the perimeter of the upper section333B. In a transverse plane, the axial pathway 337 is generally straightor flat with at least one inflection point and/or hump 329 formedtherein. The inflection point 329 and/or hump allows for an actuation orlinear actuation of a gear block (not illustrated). The inflection point329 and/or hump can also when combined with the two dimensionalrotational movement (also call a first portion of the three-dimensionalcircuit) of the gear block (not illustrated) caused by the pivotingand/or rotation of the rocker arm(s) by the cam pathway, generate thesecond portion of movement, which when combined with the first portioncreates a three dimensional circuit of movement for the gear block. Thelinear actuation of the gear block can allow for an engagement anddisengagement of the gear block (not illustrated) from the outputelement (not illustrated).

In FIG. 11, the output element 350 is illustrated in a perspective view.The output element 350 can have an output element circumferentialsurface 351. In at least one embodiment, the output elementcircumferential surface 351 can have an interface surface 353. In atleast one example, the interface surface 353 can be a set of gear teeth,while in other examples the interface surface 353 may include post andhole, tongue and groove, friction fit surface or other interfacingmeans. The output element 350 may also be secured to an output device orsystem through a securing aperture 359.

The output element 350 has a central aperture 332 coaxially aligned withthe center of the output element 350. The output element 350 may alsodefine a housing void 355 that allows for the output element 350 toreceive the axial cam (not illustrated) and the cam element (notillustrated).

With reference now to FIG. 12, a perspective view of a cam element 330is depicted. The cam element 330 can have one or more axial cam securingapertures 345 that allows for a securing of the cam element 330 with anoutput element guide and/or ball bearing assembly (or set of ballbearings) (not illustrated). The axial cam securing aperture(s) 345 canbe arranged coaxially around the central aperture 332. The cam element330 includes a planar surface 334 having at least one pathway 336 formedtherein. In at least one example, the pathway 336 will have a singledepth that is uniform along the entire pathway 336. In a preferredembodiment, the planar surface 334 of the cam assembly 330 issubstantially perpendicular to the axis of rotation of the cam assembly330. While the planar surface 334 in FIG. 12 is depicted on the side ofthe cam element 330 facing the axial cam 331, it should be understoodthat the planar surface into which pathway(s) 336 is formed may beconfigured on either facing side of the cam element 330 (i.e., either aplanar surface facing the axial cam 331 or a planar surface facing awayfrom the axial cam 331). In other examples, the pathway 336 may vary indepth along the length of the pathway 336. The pathway 336 can allow acam follower 394 (See FIGS. 5 and 15) to generate a pivot or pivotingforce on a rocker arm and/or gear block 362 (see FIG. 5). As the camfollower traverses the pathway 336 the pathway can change in directionto move a rocker arm and/or gear block coupled to the cam follower. Theaxial cam 331 (see FIGS. 9 and 10) can rest and/or be secured via one ormore fasteners to the cam element support surface 318.

FIGS. 13 and 14, illustrate an embodiment of a gear block 362. In thisembodiment, the gear block 362 is generally rectangular in shape andincludes a gear block tracking post 364. The gear block tracking post364 can allow the gear block 362 to track a pathway 337 formed in theaxial cam 331 (see FIGS. 9-10). The gear block 362 may further includean interface surface 363 for interfacing with the interface surface 353of the output element 350 (see FIG. 11). In at least one example, theinterface surface 363 comprises a set of gear teeth, while in otherexamples the interface surface 363 may include post and hole, tongue andgroove, friction fit surface or other interfacing means. The gear block362 further includes a void 311 formed in the opposing surface from thegear block interface surface 363. The gear block rotation void 311 isutilized to connect the gear block 362 to a rocker arm 399 (see FIGS. 6and 15). In at least one example, the gear block rotation void 311, canhave shoulders or contact points 311A/311B. The shoulder(s) or contactpoints 311A/311B can interact with receiving voids 397 on the rocker arm399 to allow for pivoting and/or rotation to occur. In some examples,the shoulders or contact point(s) 311A/311B and the receiving voids 397of the rocker arm 399 do not allow for the gear block 362 to rotateand/or pivot about a pivot point of the rocker arm 399.

FIGS. 15 and 16 are illustrations of one embodiment of a rocker arm 399.The rocker arm 399 can be coupled to the gear block 362 (see FIG. 5) togenerate a pivoting and/or rotational movement of the gear block 362.The rocker arm 399 is generally L-shaped, with an upper arm 398A, arotation arm 398B, and a rocker arm post or pivot point 388. The upperarm 398A may have a cam follower aperture 386 formed through the upperarm portion 398A for receiving a cam follower device 394. The upper arm398A and/or rotation arm 398B can be manufactured with an angled offset396 that allows for the gear block (not illustrated) to be rotatedand/or pivoted in a designer specified pattern. In some examples, theupper arm 398A and the rotational arm 398B, may have no offset angle 396and create an approximate right or ninety degree angle with the pivotpoint portion 388 of the rocker arm 399. The rotational arm portion 398Bof the rocker arm 399 may have a pivot pin aperture 381 that traversesthe rotational arm portion and aligns with one of the receiving voids397A and/or 397B that are defined by the rocker arm post/pivot point388. As shown in FIG. 5, the rocker arm post/pivot point 388 can beconfigured to allow a gear block 362 to be coupled to the rocker arm399. The rocker arm post/pivot point 388 can further include or defineat least one receiving void 397. In some examples, there may be tworeceiving voids 397A, and/or 397B. The receiving void 397 can allow therocker arm 399 to receive a shoulder or contact point of a gear block(not illustrated). In at least one embodiment, the receiving void(s) 397can allow for the gear block 362 to be pivoted and/or rotated around adesigner specified point in combination with other components of a gearblock mechanism. The pivot pin aperture 381 allows for a pivot pin to beplaced in a manner that would prevent a gear block from pivoting and/orrotating a specified amount by preventing the shoulder or contact pointfrom being able to be received by the receiving void 397. This allowsthe gear block to generate a driving force in a single direction, and/orprevent the gear block from rotating beyond a specified rotation amount.

With reference again to the Figures, and in particular FIG. 17, a fourthembodiment of a gearbox mechanism 420 of the present invention isdepicted. The gearbox mechanism 420 may be powered and/or rotated by apower source or actuator (as shown in FIGS. 1A and 1B), that istranslated to an output device. The power source can be an electricmotor, combustion engine, water activated source, wind turbine, or otherpossible embodiments. Additionally, the power source or actuator, aswell as the output device may be rotatively coupled by means of gears,chains, belts, or magnetic fields.

The gearbox mechanism 420 can be configured about a central axis 406.The central axis 406 can pass through a central aperture of the mainbody 440, the output element 450, cam element 430, and hub 414. The hub414 may include a ball bearing assembly (not illustrated) that allowsthe cam element 430 to rotate freely within the hub 414 based upon aninput device such as a shaft or rotatable elements such as a set ofother gearing, belts, levers, magnetic or electrical fields, etc. Themain body 440 and the hub 414 may be coupled together with fasteners(not illustrated). The fasteners may be screws, bolts, all thread,compression fit devices, or other means for fastening two componentstogether in a fixed or secure manner. The gearbox mechanism 420 mayfurther include bearings such as roller bearings 407 that may separateeach of the output element 450, and cam element 430 from the main body440 and/or the hub 414. The gearbox mechanism 420 may also include aplurality of gear block assemblies 460. Each gear block assembly caninclude a rocker arm 499 (rocker arms 499A, 499B, 499C, 499D, 499E,499F, and 499G collectively referred to as rocker arm(s) 499) that arecoupled with the gear block(s) 462 (gear blocks 462A, 462B, 462C, 462D,462E, and 462F may be referred to collectively as gear block(s) 462). Insome embodiments the gear block(s) 462 may have a pathway tracker thatcan individually or in combination with a pathway follower elementtracks and/or follows a pathway formed into the cam element 430.

The gear blocks 462 of the present invention are specifically designedto enable a greater surface area (e.g., greater number of gear teeth) toengage the output element 450 at any given time, thereby spreading thestresses associated therein across a greater area. By dramaticallyincreasing the contact area between the gear block 462 and the outputelement 450 at any given time the mechanical stress level issignificantly decreased. In addition, the gear block 462 of the presentinvention reduce backlash to zero and even preloaded conditions tocreate a tight connection between the power source and/or the powereddevice (not illustrated). This is an extremely desirable featureespecially for high vibration applications. Moreover, because thestresses associated with engagement of the gear block 462 against theoutput element 450 are distributed across a greater area, the gear block462 may be manufactured of lighter-weight materials, which are typicallyless expensive and easier to manufacture, with no degradation inreliability.

For example, per Hertz Contact Theory a typical stress result for spurgears are in the range from 450 MPa to 600 MPa. High grade steels arethe best fitted materials for handling such high stress levels. Othermaterials like low grade steel or aluminum will deform under the similarconditions. However, by distributing the stresses across a large areasof contact in accordance with the gearbox mechanism of the presentinvention, the levels of stress under the similar conditions can bereduced to about 20 MPa. These low stress levels allow the gearboxmechanism of the present invention to be manufactured using low gradesteels, aluminums or even plastics for the same application. By reducingits weight and size, the gearbox mechanism 420 of the present inventionis adaptable to a broad range of applications that were previouslyimpractical because of weight and space limitations.

In some embodiments, the rocker arm 499 can also have a cam follower 494allowing for the following of a specified pathway(s) formed along acircumferential surface of the cam element 430. The interface surfaces463 (see FIG. 23) of the gear block 462 can engage with the interfacesurface 452 of the output element 450. In some embodiments, the gearblocks are rotated by an associated movement of the rocker arm 499.

The cam element 430 includes at least one unique pathway or groove thatinterfaces with the cam follower 494 of the rocker arm 499 so that, asthe cam element 430 rotates, the movement of the gear block 462 and/orrocker arm 499 is controlled in two dimensions in accordance with atleast one certain design parameter. By varying the radius of the pathwayor grooves on the cam element 430, the gear block assemblies driverespective gear block(s) 462 through a two-dimensional circuit inresponse to rotation of the cam element 430. Broadly speaking, thetwo-dimensional circuit includes urging the gear block(s) 462 to engagethe output element 450 and move and/or rotate the output element 450 aspecified distance prior to disengaging from the output element 450, andreturning back the specified distance to again reengage the outputelement 450 once again, and repeat the process. The travel path orcircuit of each gear block 462 is controlled by adjusting the length,width, height, and/or size of the respective gear block and/or rockerarm 499 and/or altering the pathways or grooves formed in the camelement 430.

The rocker arm 499 is pivoted around a specific pivot point by the camfollower 494, which traverses the path in the cam element 430 as the camelement 430 rotates. Additionally, the gear blocks 462 may also have apathway tracker and/or pathway cam follower that follows a separate pathalong the cam element 430 that also triggers an actuation point for thegear block(s) 462. In at least one embodiment, there is at least onepivot or actuation point for both the gear block(s) 462 and the rockerarm 499 that allows each to actuate or pivot separately from each otherand while also moving in conjunction to create a specific pattern ofmovement for the gear block(s) 462. The movement of a gear block 462, inat least one example, is a cyclical, annular or closed loop movementthat may have a generally rectangular, elliptical, circular, square,conical, oval, ovoid, truncated circular pattern, or any combinationthereof, design specified pattern of movement. In some embodiments, themain body 440 may be coupled with at least one hub 412A and/or 412B. Insome examples, the hub(s) 412A and 412B may be coordinated

With reference now to FIG. 18, a perspective view is depicted of the camelement 430, along with the rocker arm 499, cam followers 494, and gearblock 462. The central axis 406 passes through the central aperture 432at the center of the cam element 430. In at least one embodiment of thepresent disclosure, as it rotates the cam element 430 interacts with therocker arm 499 along with the gear block 462 to cause the gear block 462to have a cyclical, annular or closed loop movement having a generallyrectangular, elliptical, circular, square, conical, oval, ovoid,truncated circular pattern, or any combination thereof, design specifiedpattern of movement based upon the pathways in the cam element 430 thatmay allow a cam follower 494 attached to the rocker arm 499 to traversealong the pathway and generate movement of the gear block(s) 462. In atleast one embodiment, the cam follower(s) 494 may be coupled and/orattached to the rocker arm 499 through a rocker block 470 (see FIGS. 23& 28).

Each of the cam followers 494 can each have a separate path or, in someembodiments, may have a single path that each follow at a differentposition simultaneously. The gear block(s) 462 can be pivotallyconnected to the rocker arm 499. Alternatively, or in addition, a ringspring connecting all of the gear blocks 462 in a gear train may be usedas a biasing mechanism in accordance with the present invention. In atleast one embodiment of the present disclosure, the cam element willhave a single pathway, however there maybe multiple paths formed in thecam element 430 that can be in the same plane where they are parallelpaths, or paths of different distances from the central axis 406, or thepaths can be in separate planes stacked in the direction of the centralaxis 406.

In at least one embodiment, the pathways 436, 437 along cam element 430allows for movement and rotation of the gear blocks 462 causing theinterface surfaces of the gear blocks 462 to engage, interface and/orinteract with the output element 450 (FIG. 17). As the cam element 430rotates, cam follower(s) 494 maintain contact with the surface of theirrespective pathways or grooves formed in the cam element 430. While thecam element 430 depicted in the Figures, appears to be a single unithaving at least one pathway or groove formed in the circumferentialsurface 434 of the cam element 430, it is understood that the camelement 430 may also comprise a plurality of separate discs or tubes,each having a unique pathway formed in its circumferential surface 434,which are mechanically coupled to one another to assemble a single camassembly 430.

For example, by varying the radius of the pathway or groove 436, 437 onthe cam element 430, the rocker arm 499 pivots about its pivot point tocompensate and maintain contact between rocker arm 499/cam follower 494and the pathway 436, 437. This pivoting or moving of the rocker arm 499about its pivot point induces movement in the pivotal connection withthe gear block 462. Each rocker arm 499 acts independently of the otherrocker arm(s) 499 due to the cam follower(s) 494 of each rocker arm 499following and/or traversing the pathway 436, 437 formed in thecircumferential surface of the cam element 430 at their respectivedistinct points.

As the cam followers 494 for the rocker arms 499 follow their respectivepathway(s) 436, 437 the rocker arm 499 can pivot at specific pointcausing the gear block to pivot and/or rotate around a specific point.For example, the pivot point of the rocker will trigger a left, right,in or out, or a rotational motion to the gear block 462. Associatedtogether they allow for a cyclical, annular or closed-loop movement ofthe gear block and the interfacing surface that has a generallyrectangular, elliptical, circular, square, conical, oval, ovoid,truncated circular pattern, or any combination thereof, design specifiedpattern of movement. For example, the pivot point of the rocker arm 499will trigger a left, right, in or out, or a rotational motion to thegear block 462. In general, the two-dimensional circuit may have a firstportion 439A includes urging the gear block 462 to biasing the outputelement (not illustrated) and move or rotate the output element (notillustrated) a specified distance prior to releasing the biasing of theoutput element. Additionally, there may be an engagement and/ordisengagement actuation that allows for a second portion 439B of thetwo-dimensional circuit 439. Associated together they allow for acyclical, annular or closed-loop movement or circuit 439 of the gearblock and the interfacing surface that has a generally rectangular,elliptical, circular, square, conical, oval, ovoid, truncated circularpattern, or any combination thereof, design specified pattern ofmovement. The cyclical, annular or closed-loop movement or circuit 439of the gear block 462 can allow for a positive biasing of the outputinterface surface by the gear block interface surface that is translatedinto a forward rotation of the output element 350. Additionally, thegear block 462 can negatively bias the output element interface surfacewith the gear block interface surface in a manner that reduces thebacklash or possible backlash of the output element and/or gear block.In at least one embodiment, there can also be a neutral biasing orposition that allows the gear block 462 to not bias the output elementin a positive and/or negative manner, it may also in some example allowfor the gear block 462 to release outwardly from the central axis.

FIGS. 19-20 provide illustrations of the cam element in alternativeperspective views. The cam pathways 436/437 allow for a biasing of thegear block (not illustrated) in both positive and negative directions.For example, as a cam follower (not illustrated) follows the pathwaysformed along the circumferential surface 434 of the cam element the gearblock is rotated and/or pivoted into and/or through a neutral position,a positively biased position, or a negatively biased position. In thisexample, radiuses of the pathways 436/437 allow for the gear block (notillustrated) to be cycled through a neutral position at a first pointalong the interface surface of the output element (not illustrated) to aneutral position at a second point along the interface surface of theoutput element. The neutral positions allow for an engagement and/ordisengagement to occur and allow for the gear block to be cycled from afirst engaged position to a second engaged position. The cam element 430may also have an actuation pathway 438 that may be tracked and/orfollowed by a gear block tracking post 464 (see FIG. 24) and/or a gearblock tracking follower 474 (see FIG. 23). The actuation pathway 438allows the linearly actuated based on the position of the gear blocktracker post 464 (see FIG. 24) along the actuation pathway 438. Thelinear actuation in combination with the rotational actuation(two-dimensional actuation) of the gear block results in athree-dimensional actuation. The three-dimensional combination ofmovements causes the cyclical and/or patterned movement of gear blockthat imparts a force on the output element (not illustrated) generatingmovement of said output element. As shown in FIGS. 20 and 22, in thetransverse plane, the actuation pathway 438 is generally straight orflat with at least one inflection point and/or hump 429 formed therein.The inflection point 429 and/or hump allows for an actuation or linearactuation of a gear block (not illustrated). The inflection point 429and/or hump can also allow for, when combined with the two-dimensionalcircuit of the gear block (not illustrated) caused the pivoting and/orrotation of the rocker arm(s) by the cam pathway, causes athree-dimensional circuit for the gear block. The linear actuation ofthe gear block can allow for an engagement and disengagement of the gearblock from the output element.

With reference now to FIGS. 21-29, various perspective and isometricview illustrations of a gear block assembly 460 and/or portions of agear block assembly are depicted. The gear block assembly 460 mayinclude a rocker block 470, a rocker pin 480, gear block 462, trackerfollower 474, rocker arm 499, and cam follower(s) 494A/494B. The rockerarm 499 is configured to allow the gear block 462 to be engaged and/ordisengaged with an output element (not illustrated) as the trackerfollower 474 follows an actuation pathway (not illustrated) theengagement/disengagement of the gear block 462 may be caused linear oractuation movement of the gear block 462. Additionally, the camfollower(s) 494A/494B can follow pathways that cause a two-dimensionalmovement of the gear block 462.

In at least one embodiment, the rocker arm 499, defines a rocker blockvoid 497B within the rocker arm 499. The rocker block void 497B can besized and shaped to allow it to receive a portion of the rocker block470. The rocker block 470 may have a rocker block extension 474 thatallows for the cam follower arm(s) 472A/472B to be coupled to the rockerarm 499. The cam follower arm(s) 472A/472B can have a cam followeraperture 471A/471B that is defined in the cam follower arm(s) 472A/472Band traverses through the body of each respective cam follower arm472A/472B. The rocker block 470 in at least one embodiment ismanufactured of a resilient material that does not allow for any flexingof the cam follower arm(s) 472A/472B. In at least one example, the camfollower arm(s) 472A/472B may be made of a flexible material that mayhave memory properties that prevent it from overextending and/orreturning to a specific structure or form after a flexing has occurred.

The rocker arm 499 can also define a rocker pin void 497A within therocker arm 499. The rocker pin void 497A may also include a rockersecuring pin void 498B that is sized to receive a fastener (notillustrated). The fastener (not illustrated) may be utilized to preventthe rocker pin 480 from moving once placed within the rocker pin void497A. In some embodiments, the fastener (not illustrated) may alsocouple the rocker pin 480 with the gear block 462. The gear block 462can have a pin slot 498A that allows for a fastener, or other couplingdevice, mechanism or means to couple the gear block to the rocker arm499 and/or the rocker pin 480.

The gear block 462 can include a gear block rotation void 411 thatallows for a coupling device or mechanism to interface with the pin slot498A. Additionally, the gear block rotation void 411 can also allow forthe rotation and/or pivoting of the gear block 462 based on theactuation, rotation, and/or pivoting imposed on the rocker arm 499,rocker block 470 and/or rocker pin 480. As the gear block 462 is rotatedand/or pivoted the gear block interface surface 463 can interact withother interface surfaces such as an output interface surface (notillustrated). The gear block 462 can have a gear block post 464 thatallows the gear block 462 to interface with a pathway and/or groove. Thegear block post 464 can also allow for a tracking element (notillustrated). The tracking element may be a ball bearing, rollerbearing, or other mechanism or means for reducing friction.

With reference to FIGS. 21 and 22, when the rocker arm 499 is coupledwith the rocker block 470 and/or rocker pin 480 there can be a gap orvoid 496A/496B that can be filed with a void or material to allow forcompliance mechanics. The material in some embodiments may have a memoryor alloy like effect that allow it to transfer energy between the rockerarm 499 and the rocker pin 480 or the rocker block 470. Compliancemechanics or compliance mechanisms allow for a force or energy to betransferred to another body or object through a deformation or elasticbody.

FIG. 30 is a perspective view of the main body 440. The main body 440,in at least one embodiment, houses the gear block assembly when the gearblock mechanism is assembled. The main body 440 can have a rocker armvoid 477 and a rotation or pivot void 479. The rocker arm void 477allows for the main body 440 to receive the rocker arm 499 and allow itto pivot and/or rotate about a fixed pivot point. The rotation or pivotvoid 479 allows for the rotation and/or pivoting of the gear blockassembly. In at least one example, the rotation or pivot void 479 allowsfor the gear block assembly, and/or the rocker block (not illustrated)to rotate and/or pivot into the void with the wall of the void asdefined by the main body 440, thereby preventing excessive rotation orpivoting.

It will now be evident to those skilled in the art that there has beendescribed herein an improved gearbox mechanism. Although the inventionhereof has been described by way of a preferred embodiment, it will beevident that other adaptations and modifications can be employed withoutdeparting from the spirit and scope thereof. The terms and expressionsemployed herein have been used as terms of description and not oflimitation; and thus, there is no intent of excluding equivalents, buton the contrary it is intended to cover any and all equivalents that maybe employed without departing from the spirit and scope of theinvention.

I claim:
 1. A gearbox mechanism comprising: a cam assembly removablycoupled to a rotating device, the cam assembly having an axial cam and acam, wherein the cam comprises at least one cam pathway and the axialcam comprises at least one axial pathway, and the cam assembly beingrotatable around a central axis when rotated by the rotating device; anoutput element coaxially configured with the cam assembly, and removablycoupled to an output device, wherein the output element having an outputelement interface surface on a circumferential surface of the outputelement; and at least one cam-actuated gear block assembly comprising: agear block having a gear block interface surface; a rocker arm pivotallycoupled to the gear block; a pathway tracker coupled to the gear block;and a cam follower rotatably coupled to the rocker arm.
 2. The gearboxmechanism of claim 1, wherein the cam assembly is removably coupled tothe rotating device by a fastener.
 3. The gearbox mechanism of claim 1,wherein the rocker arm is pivotally coupled to the gear block by meansof a void formed into the gear block and dimensioned to receive a postof the rocker arm.
 4. The gearbox mechanism of claim 1, wherein therocker arm is L-shaped.
 5. The gearbox mechanism of claim 1, wherein therocker arm comprises a void for receiving a rocker block, said rockerblock having at least one cam follower arm.
 6. The gearbox mechanism ofclaim 1, wherein the cam pathway is formed in a planar surface of thecam, said planar surface being substantially perpendicular to an axis ofrotation of said cam, and the axial pathway is formed in acircumferential surface of the axial cam.
 7. The gearbox mechanism ofclaim 1, wherein the cam pathway and the axial pathway are formed intoperpendicular surfaces.
 8. The gearbox mechanism of claim 1, wherein theoutput element interface surface is a set of gear teeth.
 9. The gearboxmechanism of claim 1, wherein the cam is removably coupled to the axialcam.
 10. The gearbox mechanism of claim 1, wherein the output elementinterface surface extends outwardly away from the central axis.
 11. Acam-actuated gear block assembly comprising: a gear block having a gearblock interface surface; a rocker arm pivotally coupled to the gearblock; a pathway tracker coupled to the gear block; and a cam followerrotatably coupled to the rocker arm; wherein the rocker arm has at leastone pivot point.
 12. The cam-actuated gear block assembly of claim 11,wherein the gear block interface surface extends towards a central axis.13. The cam-actuated gear block assembly of claim 11, wherein the gearblock and the rocker arm interact to cause a rotational movement of thegear block.
 14. The cam-actuated gear block assembly of claim 11,wherein the pathway tracker follows an axial pathway of a cam assembly.15. The cam-actuated gear block assembly of claim 11, wherein the camfollower follows a cam pathway of a cam assembly.
 16. The cam-actuatedgear block assembly of claim 11, wherein the gear block is engaged in alinear motion based on the position of the pathway tracker along theaxial pathway.
 17. The cam-actuated gear block assembly of claim 11,wherein the rocker arm pivots along the at least one pivot point basedon the position of the cam follower along the cam pathway.
 18. Thecam-actuated gear block assembly of claim 11, wherein gear block movesthrough a three-dimensional circuit based on pivoting of the gear block,the rocker arm, and the pathway tracker position along the axialpathway.
 19. The cam-actuated gear block assembly of claim 18, whereinsaid three-dimensional circuit is a cyclical, annular or closed loopmovement that has a rectangular, elliptical, circular, square, conical,oval, ovoid, truncated circular pattern, or any combination thereof,along with a linear movement generally perpendicular to the cyclical,annular or closed loop movement, both said movements are designspecified pattern of movement.
 20. The cam-actuated gear block assemblyof claim 11, wherein the gear block interface surface engages with anoutput element interface surface during a pattern of rotation togenerate movement of an output element.
 21. A method of operating agearbox mechanism comprising: rotating a cam assembly, said cam assemblycomprising a cam having a cam pathway, and an axial cam having an axialpathway formed in a circumferential surface of the axial cam; a camfollower coupled to a rocker arm following the cam pathway; a pathwaytracker coupled to a gear block following the axial pathway; pivoting arocker arm based on the movements of the cam follower; linearlyactuating the gear block based on the movement of the pathway trackeralong the axial pathway; moving the gear block in correlation to thepivoting of the rocker arm and the gear block, and the linear actuatingof the gear block; interfacing an interfacing surface of the gear blockwith an interfacing surface of an output element; and causing arotational movement of the output element based on the interfacing ofthe gear block and the output element.
 22. The method of operating agearbox mechanism of claim 21, wherein the cam assembly is rotated by arotating device.
 23. The method of operating a gearbox mechanism ofclaim 21, wherein the cam pathway is generally circular.
 24. The methodof operating of a gearbox mechanism claim 21, wherein the axial pathwayis generally straight in a transverse plane and includes at least oneinflection point.
 25. The method of operating a gearbox mechanism ofclaim 21, wherein the cam pathway is formed into a planar surface of thecam, said planar surface being substantially perpendicular to an axis ofrotation of the cam.
 26. The method of operating a gearbox mechanism ofclaim 21, wherein the pivoting of the gear block and the pivoting of therocker arm generate a rotational movement pattern for the gear block.27. The method of operating a gearbox mechanism of claim 21, wherein theinterfacing occurs when the gear block generally moves about a centralaxis during its pivoting.
 28. The method of operating a gearboxmechanism of claim 21, wherein the interfacing occurs when the gearblock is linearly actuated parallel to a central axis during its by itsmovement initiated by the axial cam and axial cam pathway.
 29. Themethod of operating a gearbox mechanism of claim 21, wherein the causinga rotational movement further comprises pushing the output element basedon the interfacing of the gear block and output element.
 30. The methodof operating a gearbox mechanism of claim 21, wherein the causing arotational movement further comprises biasing the output element basedon the interfacing of the gear block and the output element.